US20240084862A1 - Decoupler with torque-limiting feature to protect components thereof - Google Patents
Decoupler with torque-limiting feature to protect components thereof Download PDFInfo
- Publication number
- US20240084862A1 US20240084862A1 US18/262,343 US202218262343A US2024084862A1 US 20240084862 A1 US20240084862 A1 US 20240084862A1 US 202218262343 A US202218262343 A US 202218262343A US 2024084862 A1 US2024084862 A1 US 2024084862A1
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- United States
- Prior art keywords
- decoupler
- spring
- isolation spring
- torque
- input member
- Prior art date
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Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H7/00—Gearings for conveying rotary motion by endless flexible members
- F16H7/18—Means for guiding or supporting belts, ropes, or chains
- F16H7/20—Mountings for rollers or pulleys
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D41/00—Freewheels or freewheel clutches
- F16D41/20—Freewheels or freewheel clutches with expandable or contractable clamping ring or band
- F16D41/206—Freewheels or freewheel clutches with expandable or contractable clamping ring or band having axially adjacent coils, e.g. helical wrap-springs
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K25/00—Auxiliary drives
- B60K25/02—Auxiliary drives directly from an engine shaft
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
- F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
- F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D13/00—Friction clutches
- F16D13/76—Friction clutches specially adapted to incorporate with other transmission parts, i.e. at least one of the clutch parts also having another function, e.g. being the disc of a pulley
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
- F16D3/02—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions
- F16D3/12—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive adapted to specific functions specially adapted for accumulation of energy to absorb shocks or vibration
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D7/00—Slip couplings, e.g. slipping on overload, for absorbing shock
- F16D7/02—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type
- F16D7/022—Slip couplings, e.g. slipping on overload, for absorbing shock of the friction type with a helical band or equivalent member co-operating with a cylindrical torque limiting coupling surface
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K25/00—Auxiliary drives
- B60K25/02—Auxiliary drives directly from an engine shaft
- B60K2025/022—Auxiliary drives directly from an engine shaft by a mechanical transmission
Definitions
- This disclosure relates generally to the field of decouplers, which allow items that are operatively connected to an endless drive member (such as an engine crankshaft and input shafts for belt-drive accessories on a vehicle engine) to operate temporarily at a speed other than the speed of the endless drive member, and more particularly to carriers for decouplers, which hold both a wrap spring clutch and an isolation spring.
- an endless drive member such as an engine crankshaft and input shafts for belt-drive accessories on a vehicle engine
- a decoupler mechanism on an accessory, such as an alternator, that is driven by a belt from the crankshaft of an engine in a vehicle.
- a decoupling mechanism which may be referred to as a decoupler assembly or a decoupler, permits the associated accessory to operate temporarily at a speed that is different than the speed of the belt.
- the crankshaft undergoes cycles of accelerations and decelerations associated with the firing of the cylinders in the engine.
- the decoupler permits the alternator shaft to rotate at a relatively constant speed even though the crankshaft from the engine, and hence, the pulley of the decoupler, will be subjected to these same cycles of decelerations and accelerations, commonly referred to as rotary torsional vibrations, or torsionals.
- a carrier has been employed in decouplers for some time, where a wrap spring clutch is used.
- the carrier holds an end of a wrap spring clutch and also an end of an isolation spring, helping to keep the assembly together. It has been found, however, that failures have occurred in the carrier, over time, after many cycles of torque transfer through the decoupler. It would be advantageous to provide a decoupler that has an increased resistance to failure.
- Decouplers that are subjected to high torque transients can be more susceptible to failure than decouplers in other situations.
- An example of such a decoupler is a decoupler on an input shaft of a supercharger. As such it would be particularly advantageous to provide a decoupler with an increased resistance to failure in applications where there are high torque transients, such as decouplers mounted on the shaft of a supercharger.
- a decoupler in an aspect, includes a decoupler input member, a decoupler output member, a one-way clutch and an isolation spring.
- the decoupler input member is rotatable relative to the decoupler output member.
- the decoupler input member and the decoupler output member are rotatable about an axis.
- the one-way clutch is positioned to receive torque from the decoupler input member.
- the isolation spring is a helical torsion spring, having a first helical end and a second helical end, and has a first axial end and a second axial end, and a radially outer surface and a radially inner surface.
- the isolation spring is positioned to receive torque from the one-way clutch, and to transmit torque to the decoupler output member at least indirectly, through the second helical end.
- the isolation spring changes size radially based on how much torque is being transferred through the isolation spring.
- the decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size. Frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- FIG. 1 is an elevation view of an engine with a belt drive with a decoupler in accordance with an embodiment of the present disclosure.
- FIG. 2 is a perspective view of the decoupler shown in FIG. 1 .
- FIG. 3 A is an exploded perspective view of the decoupler shown in FIG. 2 .
- FIG. 3 B is another exploded perspective view of the decoupler shown in FIG. 2 .
- FIG. 4 is a sectional view of the decoupler shown in FIG. 2 .
- FIG. 5 A is a sectional elevation view of the decoupler shown in FIG. 2 during a low torque transfer.
- FIG. 5 B is a sectional elevation view of the decoupler shown in FIG. 2 during a high torque transfer.
- FIG. 6 is graph illustrating the relationship between torque inputted to a pulley of the decoupler and the torque transferred at a carrier in the decoupler, for both the decoupler shown in FIG. 2 and a prior art decoupler.
- FIG. 1 shows an engine 10 for a vehicle.
- the engine 10 includes a crankshaft 12 which drives an endless drive element, which may be, for example, a belt 14 .
- the engine 10 drives a plurality of accessories 16 , such as a supercharger 18 .
- Each accessory 16 includes an input drive shaft 15 with a pulley 13 thereon, which is driven by the belt 14 .
- a decoupler 20 may be provided instead of a pulley, between the belt 14 and the input shaft 15 of any one or more of the belt driven accessories 16 , and in particular the supercharger 18 .
- FIGS. 2 , 3 A and 3 B show a perspective assembled view, and two exploded perspective views respectively of the decoupler 20 .
- the decoupler 20 includes a hub 22 , a pulley 24 , a first bearing member 26 , a second bearing member 27 , an isolation spring 28 , a carrier 30 , and a wrap spring clutch 32 .
- the hub 22 may be adapted to mount to the accessory shaft 15 ( FIGS. 1 and 3 A ) in any suitable way.
- the hub 22 may have a shaft-mounting aperture 36 therethrough that is used for the mounting of the hub 22 to the end of the shaft 15 , for co-rotation of the hub 22 and the shaft 15 about an axis A ( FIG. 3 A ).
- the decoupler 20 includes a hub extension member 22 a that acts as a spacer to position the decoupler (and the pulley 24 in particular) in a selected position axially for mating with the belt 14 .
- the pulley 24 is rotatably mounted to the hub 22 .
- the pulley 24 has an outer surface 40 which is configured to engage the belt 14 .
- the outer surface 40 is shown as having grooves 42 .
- the belt 14 may thus be a multiple-V belt. It will be understood however, that the outer surface 40 of the pulley 24 may have any other suitable configuration and the belt 14 need not be a multiple-V belt.
- the pulley 24 could have a single groove and the belt 14 could be a single V belt, or the pulley 24 may have a generally flat portion for engaging a flat belt 14 .
- the pulley 24 further includes an inner surface 43 , which the wrap spring clutch 32 may engage in order to couple the pulley and hub 22 together.
- the pulley 24 may be made from any suitable material, such as a steel, or aluminum, or in some cases a polymeric material, such as certain types of nylon, phenolic or other materials. As can be seen in FIG. 3 A , the pulley 24 has a proximal end 46 (i.e. an end that is closer to the accessory to which the pulley 24 is mounted), and a distal end 47 (i.e. an end that is farther from the accessory to which the pulley 24 is mounted).
- proximal end 46 i.e. an end that is closer to the accessory to which the pulley 24 is mounted
- distal end 47 i.e. an end that is farther from the accessory to which the pulley 24 is mounted.
- the first bearing member 26 rotatably supports the pulley 24 on the hub 22 at the proximal axial end 46 of the pulley 24 .
- the first bearing member 26 may be any suitable type of bearing member, such as a ball bearing.
- a first retainer 45 is provided, which mounts into a groove of the pulley 24 to hold the first bearing member 26 in place.
- the first retainer 45 may be, for example, a removable C-clip, as shown, or any other suitable kind of retainer.
- the second bearing member 27 is positioned at the distal end 47 of the pulley 24 so as to rotatably support the pulley 24 on a pulley support surface 48 of the hub 22 .
- the second bearing member 27 may mount to the pulley 24 and to the hub 22 in any suitable ways.
- the second bearing member 27 may be molded around the pulley support surface 48 by an injection molding process wherein the hub 22 forms part of the mold.
- the hub 22 may have a coating thereon prior to insertion into the mold cavity, to prevent strong adherence of the bearing member 27 to the pulley support surface 48 during the molding process, so that after removal of the hub 22 and bearing member 27 from the molding machine (not shown), the bearing member 27 can rotate about the hub 22 .
- other ways of joining the second bearing member 27 and the pulley 24 may be employed, such as adhesive bonding, and/or using mechanical joining elements (e.g. resilient locking tabs) that would lock the bearing member 27 to the pulley.
- the isolation spring 28 is provided to accommodate oscillations in the speed of the belt 14 relative to the shaft 15 .
- the isolation spring 28 may be a helical torsion spring that has a first helical end 50 that is held on a helical support surface 55 and that abuts a radially extending driver wall 52 ( FIG. 4 ) on the carrier 30 .
- the isolation spring 28 has a second helical end 53 ( FIG. 3 B ) that engages a similar driver wall 57 (a small portion of which is visible in FIG. 3 A ) on the hub 22 .
- the isolation spring 28 has a plurality of coils 58 between the first and second ends 50 and 53 .
- the coils 58 are preferably spaced apart by a selected amount and the isolation spring 28 is preferably under a selected amount of axial compression installed in the decoupler 20 , which urges the isolation spring 28 to keep a position in which the first and second helical ends 50 and 53 are abutted with the respective driver walls 52 and 57 on the carrier 30 and hub 22 .
- An example of a suitable engagement between the isolation spring 28 , the hub 22 and the carrier 30 is shown and described in U.S. Pat. No. 7,712,592, the contents of which are incorporated herein by reference.
- the isolation spring 28 is positioned to receive torque from the wrap spring clutch 32 , and to transmit torque to the hub 22 at least indirectly.
- a thrust plate 73 may be provided to receive the axial thrust force of the carrier 30 resulting from the axial compression of the isolation spring 28 .
- a second retainer 75 may be provided between the thrust plate 73 and the first bearing member 26 .
- a partial cover 100 is mountable to the pulley to inhibit dust and debris from migrating into the decoupler 20 during operation.
- the isolation spring 28 may be made from any suitable material, such as a suitable spring steel.
- the isolation spring 28 may have any suitable cross-sectional shape.
- the isolation spring 28 is shown as having a generally rounded rectangular cross-sectional shape, which provides it with a relatively high torsional resistance (i.e. spring rate) for a given occupied volume.
- spring rate torsional resistance
- a suitable spring rate may be obtained with other cross-sectional shapes, such as a circular cross-sectional shape or a square cross-sectional shape.
- the isolation spring 28 changes size radially based on how much torque is being transferred through the isolation spring 28 .
- the isolation spring 28 expands radially as torque transfer therethrough increases.
- a sleeve 66 may optionally be provided to ensure separation of the isolation spring 28 and the wrap spring clutch 32 during radial expansion of the isolation spring 28 .
- the wrap spring clutch 32 is positioned to receive torque from the pulley 24 .
- the wrap spring clutch 32 is generally helical, and has a first end 51 that is engageable with the first helical end 50 of the isolation spring 28 for torque transfer therewith.
- the first end 51 of the wrap spring clutch 32 may be fixedly connected to the carrier 30 , by having one or more bends (e.g. shown at 51 a ), which tightly engage a carrier slot 102 in the carrier 30 , which is complementary to the first end 51 of the wrap spring clutch 32 .
- the bent shape of the first end 51 and its engagement with the slot 102 prevents withdrawal of the first end 51 from the slot 102 .
- the wrap spring clutch 32 also has a second end 59 that may be free floating.
- the carrier 30 itself may be made from any suitable material such as, for example, a suitable nylon or the like.
- the slot 102 has a slot exit 104 through which the wrap spring clutch 32 exits from the slot 102 to wrap around an exterior of the carrier 30 (shown at 106 ).
- the slot exit 104 is defined on a radially exterior side thereof by an end wall 108 of the carrier 30 . As can be seen in FIGS. 4 , 5 A, and 6 , the end wall 108 is only supported at its base, to the rest of the carrier 30 .
- the first end 51 of the wrap spring clutch 32 transmits the torque from the pulley 24 to the hub 22 through the isolation spring 28 .
- the hub 22 is brought up to the speed of the pulley 24 .
- the wrap spring clutch 32 operatively connects the pulley 24 to the carrier 30 and therefore to the hub 22 .
- the first end 51 of the wrap spring clutch 32 is positioned to apply a clutch-related radial force on the end wall 108
- the isolation spring 28 is positioned to apply an isolation spring-related force on the carrier 30 that is at least partially opposed to the clutch-related radial force.
- the clutch-related radial force is a distributed force, a part of which is applied to the end wall 108 . This can lead to a fatigue failure of the end wall 108 over time due to repeated application of this clutch-related radial force thereon. Other stresses that are incurred by the carrier 30 can also lead to failure of the carrier 30 in other ways. Deformation or failure of the carrier 30 can lead to failure of the decoupler 20 , or at least can lead to a shortened operating life for the decoupler 20 .
- the pulley 24 includes a radial projection 150 (shown best in FIGS. 5 A and 5 B ) that is positioned to frictionally engage the radially outer surface (shown at 152 ) of the isolation spring 28 when the isolation spring 28 reaches a selected radial size (i.e. when the isolation spring 28 transmits a selected amount of torque).
- the frictional engagement of the radial projection 150 with the isolation spring 28 generates torque transfer directly from the pulley 24 to the isolation spring 28 , which is in parallel with the torque transfer that takes place from the pulley 24 to the isolation spring 28 through the wrap spring clutch 32 .
- FIG. 5 A shows the torque transfer path (at 154 ) through the decoupler 20 , when the torque being transferred is sufficiently small that the torque has not caused the isolation spring 28 to expand radially enough to engage the radial projection 150 .
- the torque transfer path 154 passes from the pulley 24 , to the wrap spring clutch 32 , to the carrier 30 , to the isolation spring 28 , and from the hub 22 (and the hub extension 22 a ) into the shaft 15 of the accessory (not shown in FIGS. 5 A and 5 B ).
- the hub extension 22 a may itself, for simplicity, be considered to be part of the hub 22 .
- FIG. 5 B shows the torque transfer path (at 156 ) through the decoupler 20 , when the torque being transferred is sufficiently large that the torque has caused the isolation spring 28 to expand radially enough to engage the radial projection 150 .
- the torque transfer path 154 continues to be present. However, some portion of the torque is transferred directly from the pulley 24 into the isolation spring 28 through the radial projection 150 , via the torque path shown at 156 in FIG. 5 B .
- the isolation spring 28 presses more and more firmly against the radial projection 150 , which increases the frictional force therebetween, which in turn increases the amount of torque that is transferred directly to the isolation spring 28 from the pulley 24 through the radial projection 150 .
- FIG. 6 shows a graph with two curves 160 and 162 that show the relationship between the torque that is inputted to the pulley 24 via the belt 14 and the torque that is transferred through the carrier 30 , for the decoupler 20 (curve 160 ) and for a decoupler of the prior art (curve 162 ).
- the curves 160 and 162 are superimposed for torques below a selected torque, which in the present example is about 26 Nm.
- the prior art decoupler has a torque transfer that continues linearly in a one-to-one relationship, since all the torque being inputted to the pulley continues to pass through the carrier.
- the decoupler 20 For the decoupler 20 , however, additional torque that is inputted to the pulley 24 , is partly transferred through the carrier 30 , and partly transferred directly through the radial projection into the isolation spring 28 . As a result, in the example graph shown, the decoupler 20 is capable of transmitting, for example, 50 nm, while only about 30 Nm passes from the wrap spring clutch 32 to the isolation spring 28 through the carrier 30 .
- the pulley 24 and the hub 22 are merely examples of a suitable decoupler input member and a suitable decoupler output member, any suitable decoupler input member and decoupler output member may be provided.
- the pulley 24 would constitute a decoupler output member and the hub 22 that mounts to the crankshaft 12 would constitute a decoupler input member.
- the wrap spring clutch 32 is just one example of a one-way clutch that may be used in the decoupler 20 . It is alternatively possible to use any other suitable type of one-way clutch such as a roller clutch or a sprag clutch, which may transfer torque to the isolation spring with or without the presence of a carrier like the carrier 30 . While the carrier 30 in the present embodiment benefits from the presence of the radial projection, it is alternatively possible to provide a benefit to a decoupler that does not have a carrier 30 , since reducing the torque transfer through the one-way clutch itself permits one to select a one-way clutch that has a lower maximum strength.
- the radial projection projects inwardly from the pulley 24 (i.e. from the decoupler input member), and engages a radially outer surface of the isolation spring 28 .
- the isolation spring 28 is configured to expand radially as torque transfer therethrough increases.
- the isolation spring contracts radially as torque transfer therethrough increases, and where the decoupler input member has a radial projection that extends radially outwards therefrom that is positioned to engage the isolation spring at a selected amount of torque transfer through the isolation spring.
- the decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size, wherein, frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- the decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size, wherein, frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- a decoupler is shown in the figures and described herein.
- the decoupler may be for an accessory drive for an engine, and in particular for a vehicular engine as shown, or for any other suitable type of engine.
Abstract
In an aspect, a decoupler is provided and includes an input member, an output member, a one-way clutch and an isolation spring. The one-way clutch receives torque from the input member. The isolation spring is helical, having a first helical end and a second helical end, and has first and second axial ends, and radially outer and inner surfaces. The isolation spring receives torque from the clutch, and transmits torque to the output member. The isolation spring changes size radially based on torque. The input member includes a radial projection that is positioned to frictionally engage one of the radially outer and inner surfaces of the spring when the spring reaches a selected size. Frictional engagement of the radial projection with the spring generates torque transfer directly from the input member to the spring in parallel with torque transfer from the input member to the spring through the clutch.
Description
- This application claims the benefit of U.S. Provisional Application No. 63/139,607, filed Jan. 20, 2021, the contents of which are incorporated herein by reference in their entirety.
- This disclosure relates generally to the field of decouplers, which allow items that are operatively connected to an endless drive member (such as an engine crankshaft and input shafts for belt-drive accessories on a vehicle engine) to operate temporarily at a speed other than the speed of the endless drive member, and more particularly to carriers for decouplers, which hold both a wrap spring clutch and an isolation spring.
- It is known to provide a decoupler mechanism on an accessory, such as an alternator, that is driven by a belt from the crankshaft of an engine in a vehicle. Such a decoupling mechanism, which may be referred to as a decoupler assembly or a decoupler, permits the associated accessory to operate temporarily at a speed that is different than the speed of the belt. As is known, the crankshaft undergoes cycles of accelerations and decelerations associated with the firing of the cylinders in the engine. The decoupler permits the alternator shaft to rotate at a relatively constant speed even though the crankshaft from the engine, and hence, the pulley of the decoupler, will be subjected to these same cycles of decelerations and accelerations, commonly referred to as rotary torsional vibrations, or torsionals.
- A carrier has been employed in decouplers for some time, where a wrap spring clutch is used. The carrier holds an end of a wrap spring clutch and also an end of an isolation spring, helping to keep the assembly together. It has been found, however, that failures have occurred in the carrier, over time, after many cycles of torque transfer through the decoupler. It would be advantageous to provide a decoupler that has an increased resistance to failure.
- Decouplers that are subjected to high torque transients can be more susceptible to failure than decouplers in other situations. An example of such a decoupler, is a decoupler on an input shaft of a supercharger. As such it would be particularly advantageous to provide a decoupler with an increased resistance to failure in applications where there are high torque transients, such as decouplers mounted on the shaft of a supercharger.
- In an aspect, a decoupler is provided and includes a decoupler input member, a decoupler output member, a one-way clutch and an isolation spring. The decoupler input member is rotatable relative to the decoupler output member. The decoupler input member and the decoupler output member are rotatable about an axis. The one-way clutch is positioned to receive torque from the decoupler input member. The isolation spring is a helical torsion spring, having a first helical end and a second helical end, and has a first axial end and a second axial end, and a radially outer surface and a radially inner surface. The isolation spring is positioned to receive torque from the one-way clutch, and to transmit torque to the decoupler output member at least indirectly, through the second helical end. The isolation spring changes size radially based on how much torque is being transferred through the isolation spring. The decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size. Frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- The foregoing and other aspects of the invention will be better appreciated with reference to the attached drawings, as follows:
-
FIG. 1 is an elevation view of an engine with a belt drive with a decoupler in accordance with an embodiment of the present disclosure. -
FIG. 2 is a perspective view of the decoupler shown inFIG. 1 . -
FIG. 3A is an exploded perspective view of the decoupler shown inFIG. 2 . -
FIG. 3B is another exploded perspective view of the decoupler shown inFIG. 2 . -
FIG. 4 is a sectional view of the decoupler shown inFIG. 2 . -
FIG. 5A is a sectional elevation view of the decoupler shown inFIG. 2 during a low torque transfer. -
FIG. 5B is a sectional elevation view of the decoupler shown inFIG. 2 during a high torque transfer. -
FIG. 6 is graph illustrating the relationship between torque inputted to a pulley of the decoupler and the torque transferred at a carrier in the decoupler, for both the decoupler shown inFIG. 2 and a prior art decoupler. - Reference is made to
FIG. 1 , which shows anengine 10 for a vehicle. Theengine 10 includes acrankshaft 12 which drives an endless drive element, which may be, for example, abelt 14. Via thebelt 14, theengine 10 drives a plurality ofaccessories 16, such as asupercharger 18. Eachaccessory 16 includes aninput drive shaft 15 with apulley 13 thereon, which is driven by thebelt 14. Adecoupler 20 may be provided instead of a pulley, between thebelt 14 and theinput shaft 15 of any one or more of the belt drivenaccessories 16, and in particular thesupercharger 18. - Reference is made to
FIGS. 2, 3A and 3B , which show a perspective assembled view, and two exploded perspective views respectively of thedecoupler 20. Thedecoupler 20 includes ahub 22, apulley 24, a first bearingmember 26, a second bearingmember 27, anisolation spring 28, acarrier 30, and awrap spring clutch 32. - The
hub 22 may be adapted to mount to the accessory shaft 15 (FIGS. 1 and 3A ) in any suitable way. For example, thehub 22 may have a shaft-mounting aperture 36 therethrough that is used for the mounting of thehub 22 to the end of theshaft 15, for co-rotation of thehub 22 and theshaft 15 about an axis A (FIG. 3A ). In the embodiment shown, thedecoupler 20 includes ahub extension member 22 a that acts as a spacer to position the decoupler (and thepulley 24 in particular) in a selected position axially for mating with thebelt 14. - The
pulley 24 is rotatably mounted to thehub 22. Thepulley 24 has anouter surface 40 which is configured to engage thebelt 14. Theouter surface 40 is shown as having grooves 42. Thebelt 14 may thus be a multiple-V belt. It will be understood however, that theouter surface 40 of thepulley 24 may have any other suitable configuration and thebelt 14 need not be a multiple-V belt. For example, thepulley 24 could have a single groove and thebelt 14 could be a single V belt, or thepulley 24 may have a generally flat portion for engaging aflat belt 14. Thepulley 24 further includes aninner surface 43, which thewrap spring clutch 32 may engage in order to couple the pulley andhub 22 together. Thepulley 24 may be made from any suitable material, such as a steel, or aluminum, or in some cases a polymeric material, such as certain types of nylon, phenolic or other materials. As can be seen inFIG. 3A , thepulley 24 has a proximal end 46 (i.e. an end that is closer to the accessory to which thepulley 24 is mounted), and a distal end 47 (i.e. an end that is farther from the accessory to which thepulley 24 is mounted). - The first bearing
member 26 rotatably supports thepulley 24 on thehub 22 at the proximalaxial end 46 of thepulley 24. The first bearingmember 26 may be any suitable type of bearing member, such as a ball bearing. Afirst retainer 45 is provided, which mounts into a groove of thepulley 24 to hold the first bearingmember 26 in place. Thefirst retainer 45 may be, for example, a removable C-clip, as shown, or any other suitable kind of retainer. - The
second bearing member 27 is positioned at thedistal end 47 of thepulley 24 so as to rotatably support thepulley 24 on apulley support surface 48 of thehub 22. Thesecond bearing member 27 may mount to thepulley 24 and to thehub 22 in any suitable ways. In the embodiment shown, thesecond bearing member 27 may be molded around thepulley support surface 48 by an injection molding process wherein thehub 22 forms part of the mold. Thehub 22 may have a coating thereon prior to insertion into the mold cavity, to prevent strong adherence of the bearingmember 27 to thepulley support surface 48 during the molding process, so that after removal of thehub 22 and bearingmember 27 from the molding machine (not shown), the bearingmember 27 can rotate about thehub 22. It will be noted that other ways of joining thesecond bearing member 27 and thepulley 24 may be employed, such as adhesive bonding, and/or using mechanical joining elements (e.g. resilient locking tabs) that would lock the bearingmember 27 to the pulley. - The
isolation spring 28 is provided to accommodate oscillations in the speed of thebelt 14 relative to theshaft 15. Theisolation spring 28 may be a helical torsion spring that has a firsthelical end 50 that is held on ahelical support surface 55 and that abuts a radially extending driver wall 52 (FIG. 4 ) on thecarrier 30. Theisolation spring 28 has a second helical end 53 (FIG. 3B ) that engages a similar driver wall 57 (a small portion of which is visible inFIG. 3A ) on thehub 22. In the embodiment shown, theisolation spring 28 has a plurality ofcoils 58 between the first and second ends 50 and 53. Thecoils 58 are preferably spaced apart by a selected amount and theisolation spring 28 is preferably under a selected amount of axial compression installed in thedecoupler 20, which urges theisolation spring 28 to keep a position in which the first and second helical ends 50 and 53 are abutted with therespective driver walls carrier 30 andhub 22. An example of a suitable engagement between theisolation spring 28, thehub 22 and thecarrier 30 is shown and described in U.S. Pat. No. 7,712,592, the contents of which are incorporated herein by reference. - The
isolation spring 28 is positioned to receive torque from thewrap spring clutch 32, and to transmit torque to thehub 22 at least indirectly. - A
thrust plate 73 may be provided to receive the axial thrust force of thecarrier 30 resulting from the axial compression of theisolation spring 28. Asecond retainer 75 may be provided between thethrust plate 73 and thefirst bearing member 26. Apartial cover 100 is mountable to the pulley to inhibit dust and debris from migrating into thedecoupler 20 during operation. - The
isolation spring 28 may be made from any suitable material, such as a suitable spring steel. Theisolation spring 28 may have any suitable cross-sectional shape. In the figures, theisolation spring 28 is shown as having a generally rounded rectangular cross-sectional shape, which provides it with a relatively high torsional resistance (i.e. spring rate) for a given occupied volume. However, a suitable spring rate may be obtained with other cross-sectional shapes, such as a circular cross-sectional shape or a square cross-sectional shape. - The
isolation spring 28 changes size radially based on how much torque is being transferred through theisolation spring 28. In the embodiment shown, theisolation spring 28 expands radially as torque transfer therethrough increases. Asleeve 66 may optionally be provided to ensure separation of theisolation spring 28 and thewrap spring clutch 32 during radial expansion of theisolation spring 28. - The
wrap spring clutch 32 is positioned to receive torque from thepulley 24. Thewrap spring clutch 32 is generally helical, and has afirst end 51 that is engageable with the firsthelical end 50 of theisolation spring 28 for torque transfer therewith. Thefirst end 51 of thewrap spring clutch 32 may be fixedly connected to thecarrier 30, by having one or more bends (e.g. shown at 51 a), which tightly engage a carrier slot 102 in thecarrier 30, which is complementary to thefirst end 51 of thewrap spring clutch 32. The bent shape of thefirst end 51 and its engagement with the slot 102 prevents withdrawal of thefirst end 51 from the slot 102. Thewrap spring clutch 32 also has asecond end 59 that may be free floating. - The
carrier 30 itself may be made from any suitable material such as, for example, a suitable nylon or the like. The slot 102 has aslot exit 104 through which thewrap spring clutch 32 exits from the slot 102 to wrap around an exterior of the carrier 30 (shown at 106). Theslot exit 104 is defined on a radially exterior side thereof by anend wall 108 of thecarrier 30. As can be seen inFIGS. 4, 5A, and 6 , theend wall 108 is only supported at its base, to the rest of thecarrier 30. - When a torque is applied from the
belt 14 to thepulley 24 to drive thepulley 24 at a speed that is faster than that of theshaft 15, friction between theinner surface 43 of thepulley 24 and the coils of thewrap spring clutch 32 drives at least one of the coils of thewrap spring clutch 32 at least some angle in a first rotational direction about the axis A, relative to thefirst end 51 of thewrap spring clutch 32. The relative movement between the one or more coils driven by thepulley 24 relative to thefirst end 51 causes the clutch spring to expand radially, which further strengthens the grip between the coils of thewrap spring clutch 32 and theinner surface 43 of thepulley 24. As a result, thefirst end 51 of thewrap spring clutch 32 transmits the torque from thepulley 24 to thehub 22 through theisolation spring 28. As a result, thehub 22 is brought up to the speed of thepulley 24. Thus, when thepulley 24 rotates faster than thehub 22, thewrap spring clutch 32 operatively connects thepulley 24 to thecarrier 30 and therefore to thehub 22. - During torque transfer through the
decoupler 20 between thepulley 24 and thehub 22, thefirst end 51 of thewrap spring clutch 32 is positioned to apply a clutch-related radial force on theend wall 108, and theisolation spring 28 is positioned to apply an isolation spring-related force on thecarrier 30 that is at least partially opposed to the clutch-related radial force. - In general, the clutch-related radial force is a distributed force, a part of which is applied to the
end wall 108. This can lead to a fatigue failure of theend wall 108 over time due to repeated application of this clutch-related radial force thereon. Other stresses that are incurred by thecarrier 30 can also lead to failure of thecarrier 30 in other ways. Deformation or failure of thecarrier 30 can lead to failure of thedecoupler 20, or at least can lead to a shortened operating life for thedecoupler 20. - In order to reduce the likelihood of deformation or failure of the
carrier 30, thepulley 24 includes a radial projection 150 (shown best inFIGS. 5A and 5B ) that is positioned to frictionally engage the radially outer surface (shown at 152) of theisolation spring 28 when theisolation spring 28 reaches a selected radial size (i.e. when theisolation spring 28 transmits a selected amount of torque). The frictional engagement of theradial projection 150 with theisolation spring 28 generates torque transfer directly from thepulley 24 to theisolation spring 28, which is in parallel with the torque transfer that takes place from thepulley 24 to theisolation spring 28 through thewrap spring clutch 32. -
FIG. 5A shows the torque transfer path (at 154) through thedecoupler 20, when the torque being transferred is sufficiently small that the torque has not caused theisolation spring 28 to expand radially enough to engage theradial projection 150. As can be seen, thetorque transfer path 154 passes from thepulley 24, to thewrap spring clutch 32, to thecarrier 30, to theisolation spring 28, and from the hub 22 (and thehub extension 22 a) into theshaft 15 of the accessory (not shown inFIGS. 5A and 5B ). Thehub extension 22 a may itself, for simplicity, be considered to be part of thehub 22. -
FIG. 5B shows the torque transfer path (at 156) through thedecoupler 20, when the torque being transferred is sufficiently large that the torque has caused theisolation spring 28 to expand radially enough to engage theradial projection 150. As can be seen, thetorque transfer path 154 continues to be present. However, some portion of the torque is transferred directly from thepulley 24 into theisolation spring 28 through theradial projection 150, via the torque path shown at 156 inFIG. 5B . As the torque that is inputted to thepulley 24 from thebelt 14 further increases, theisolation spring 28 presses more and more firmly against theradial projection 150, which increases the frictional force therebetween, which in turn increases the amount of torque that is transferred directly to theisolation spring 28 from thepulley 24 through theradial projection 150. -
FIG. 6 shows a graph with twocurves pulley 24 via thebelt 14 and the torque that is transferred through thecarrier 30, for the decoupler 20 (curve 160) and for a decoupler of the prior art (curve 162). As can be seen, thecurves decoupler 20, however, additional torque that is inputted to thepulley 24, is partly transferred through thecarrier 30, and partly transferred directly through the radial projection into theisolation spring 28. As a result, in the example graph shown, thedecoupler 20 is capable of transmitting, for example, 50 nm, while only about 30 Nm passes from thewrap spring clutch 32 to theisolation spring 28 through thecarrier 30. - The
pulley 24 and thehub 22 are merely examples of a suitable decoupler input member and a suitable decoupler output member, any suitable decoupler input member and decoupler output member may be provided. In some embodiments, for example, such as an embodiment in which thedecoupler 20 is mounted to thecrankshaft 12, thepulley 24 would constitute a decoupler output member and thehub 22 that mounts to thecrankshaft 12 would constitute a decoupler input member. - The
wrap spring clutch 32 is just one example of a one-way clutch that may be used in thedecoupler 20. It is alternatively possible to use any other suitable type of one-way clutch such as a roller clutch or a sprag clutch, which may transfer torque to the isolation spring with or without the presence of a carrier like thecarrier 30. While thecarrier 30 in the present embodiment benefits from the presence of the radial projection, it is alternatively possible to provide a benefit to a decoupler that does not have acarrier 30, since reducing the torque transfer through the one-way clutch itself permits one to select a one-way clutch that has a lower maximum strength. - In the present example, the radial projection projects inwardly from the pulley 24 (i.e. from the decoupler input member), and engages a radially outer surface of the
isolation spring 28. Additionally, theisolation spring 28 is configured to expand radially as torque transfer therethrough increases. However, it is alternatively possible to provide an embodiment in which the isolation spring contracts radially as torque transfer therethrough increases, and where the decoupler input member has a radial projection that extends radially outwards therefrom that is positioned to engage the isolation spring at a selected amount of torque transfer through the isolation spring. - The decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size, wherein, frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- Accordingly, it may be said broadly that, the decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size, wherein, frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
- A decoupler is shown in the figures and described herein. The decoupler may be for an accessory drive for an engine, and in particular for a vehicular engine as shown, or for any other suitable type of engine.
- While the description contained herein constitutes a plurality of embodiments of the present invention, it will be appreciated that the present invention is susceptible to further modification and change without departing from the fair meaning of the accompanying claims.
Claims (4)
1. A decoupler, comprising:
a decoupler input member;
a decoupler output member, wherein the decoupler input member is rotatable relative to the decoupler output member, and wherein the decoupler input member and the decoupler output member are rotatable about an axis;
a one-way clutch positioned to receive torque from the decoupler input member; and
an isolation spring that is a helical torsion spring, having a first helical end and a second helical end, and having a first axial end and a second axial end, and having a radially outer surface and a radially inner surface, wherein the isolation spring is positioned to receive torque from the one-way clutch, and to transmit torque to the decoupler output member at least indirectly, through the second helical end, wherein the isolation spring changes size radially based on how much torque is being transferred through the isolation spring,
wherein the decoupler input member includes a radial projection that is positioned to frictionally engage one of the radially outer and radially inner surfaces of the isolation spring when the isolation spring reaches a selected radial size, wherein, frictional engagement of the radial projection with the isolation spring generates torque transfer directly from the decoupler input member to the isolation spring in parallel with torque transfer from the decoupler input member to the isolation spring through the one-way clutch.
2. The clutched device as claimed in claim 1 , wherein the one-way clutch is a wrap spring clutch having a radially outer surface and a radially inner surface, wherein one of the radially outer surface and the radially inner surface is frictionally engaged with the decoupler input member during torque transfer from the decoupler input member to the wrap spring clutch, wherein the wrap spring clutch has a first helical end, and
wherein the clutched device further comprises a carrier that is positioned to hold the first helical end of the isolation spring and the first helical end of the wrap spring clutch for torque transfer therebetween.
3. The clutched device as claimed in claim 1 , wherein the one-way clutch and the isolation spring are metallic and the carrier is polymeric.
4. The clutched device as claimed in claim 1 , wherein the decoupler input member is a pulley and the decoupler output member is a hub that is shaped to mount to a shaft of an accessory.
Priority Applications (1)
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US18/262,343 US20240084862A1 (en) | 2021-01-20 | 2022-01-20 | Decoupler with torque-limiting feature to protect components thereof |
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US202163139607P | 2021-01-20 | 2021-01-20 | |
US18/262,343 US20240084862A1 (en) | 2021-01-20 | 2022-01-20 | Decoupler with torque-limiting feature to protect components thereof |
PCT/CA2022/050086 WO2022155746A1 (en) | 2021-01-20 | 2022-01-20 | Decoupler with torque-limiting feature to protect components thereof |
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US20240084862A1 true US20240084862A1 (en) | 2024-03-14 |
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US18/262,343 Pending US20240084862A1 (en) | 2021-01-20 | 2022-01-20 | Decoupler with torque-limiting feature to protect components thereof |
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US (1) | US20240084862A1 (en) |
EP (1) | EP4281678A1 (en) |
CN (1) | CN116648368A (en) |
WO (1) | WO2022155746A1 (en) |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7766774B2 (en) * | 2005-02-03 | 2010-08-03 | Litens Automotive Partnership | Torque limited decoupler |
US7878315B2 (en) * | 2006-04-14 | 2011-02-01 | Ntn Corporation | Spring clutch |
US9611903B2 (en) * | 2012-06-20 | 2017-04-04 | Mitsuboshi Belting Ltd. | Pulley structure |
US10816041B2 (en) * | 2015-12-08 | 2020-10-27 | Schaeffler Technologies AG & Co. KG | Belt pulley decoupler |
US11028884B2 (en) * | 2018-07-20 | 2021-06-08 | Gates Corporation | Isolating decoupler |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2005057037A1 (en) * | 2003-12-09 | 2005-06-23 | Litens Automotive Partnership | Spring travel limitor for overrunning decoupler |
BRPI0710286B1 (en) * | 2006-04-26 | 2019-05-07 | Litens Automotive Partnership | UNIDIRECTIONAL INSULATOR TO TRANSFER TORQUE BETWEEN A FLEXIBLE DRIVE AND A DIPOSITIVE |
US9046133B2 (en) * | 2010-11-09 | 2015-06-02 | Litens Automotive Partnership | Decoupler assembly having limited overrunning capability |
-
2022
- 2022-01-20 WO PCT/CA2022/050086 patent/WO2022155746A1/en active Application Filing
- 2022-01-20 CN CN202280008420.7A patent/CN116648368A/en active Pending
- 2022-01-20 US US18/262,343 patent/US20240084862A1/en active Pending
- 2022-01-20 EP EP22741987.6A patent/EP4281678A1/en active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7766774B2 (en) * | 2005-02-03 | 2010-08-03 | Litens Automotive Partnership | Torque limited decoupler |
US7878315B2 (en) * | 2006-04-14 | 2011-02-01 | Ntn Corporation | Spring clutch |
US9611903B2 (en) * | 2012-06-20 | 2017-04-04 | Mitsuboshi Belting Ltd. | Pulley structure |
US10816041B2 (en) * | 2015-12-08 | 2020-10-27 | Schaeffler Technologies AG & Co. KG | Belt pulley decoupler |
US11028884B2 (en) * | 2018-07-20 | 2021-06-08 | Gates Corporation | Isolating decoupler |
Also Published As
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EP4281678A1 (en) | 2023-11-29 |
WO2022155746A1 (en) | 2022-07-28 |
CN116648368A (en) | 2023-08-25 |
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